JPH0758051B2 - Supercharged multi-cylinder reciprocating piston internal combustion engine with multiple exhaust gas turbine superchargers operating in parallel - Google Patents

Supercharged multi-cylinder reciprocating piston internal combustion engine with multiple exhaust gas turbine superchargers operating in parallel

Info

Publication number
JPH0758051B2
JPH0758051B2 JP62505593A JP50559387A JPH0758051B2 JP H0758051 B2 JPH0758051 B2 JP H0758051B2 JP 62505593 A JP62505593 A JP 62505593A JP 50559387 A JP50559387 A JP 50559387A JP H0758051 B2 JPH0758051 B2 JP H0758051B2
Authority
JP
Japan
Prior art keywords
exhaust gas
gas turbine
cylinder
internal combustion
combustion engine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
JP62505593A
Other languages
Japanese (ja)
Other versions
JPH02500042A (en
Inventor
リューツ、ゲオルグ
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Rolls Royce Solutions GmbH
Original Assignee
MTU Friedrichshafen GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by MTU Friedrichshafen GmbH filed Critical MTU Friedrichshafen GmbH
Publication of JPH02500042A publication Critical patent/JPH02500042A/en
Publication of JPH0758051B2 publication Critical patent/JPH0758051B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
    • F02D17/02—Cutting-out
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/44—Passages conducting the charge from the pump to the engine inlet, e.g. reservoirs
    • F02B33/446—Passages conducting the charge from the pump to the engine inlet, e.g. reservoirs having valves for admission of atmospheric air to engine, e.g. at starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
    • F01N13/107—More than one exhaust manifold or exhaust collector
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)

Description

【発明の詳細な説明】 本発明は、「請求の範囲」第１項の上位概念による並列
的に作動をする多数の排ガスタービン過給機を有する過
給多シリンダ往復動ピストン内燃機関に関するものであ
る。このような配置により、往復動ピストン内燃機関の
運転状態に適合された最善の過給空気の装入が達成され
る。The present invention relates to a supercharged multi-cylinder reciprocating piston internal combustion engine having a number of exhaust gas turbine superchargers operating in parallel according to the general concept of "claims". is there. With such an arrangement, the optimum charging of the supercharged air adapted to the operating conditions of the reciprocating piston internal combustion engine is achieved.

ドイツ特許第23 38 952号明細書から、内燃機関の各シ
リンダ列に１個の排ガスタービン過給機が付属されてい
る上述の種類の往復動ピストン内燃機関が公知となって
いる。潤滑油の損失を最少とするために、排ガスタービ
ン過給機の回転子に、往復動ピストン内燃機関の装入空
気管路から圧縮空気が供給される、いわゆる、封鎖空気
シールが配置されている。内燃機関の一つのシリンダ列
への燃料の供給の遮断の際に、所属される排ガスタービ
ン過給機は、タービンへの排ガスの供給の遮断により停
止される。燃料の供給を遮断された、圧縮機として駆動
されるシリンダ列への空気の供給は、運転を継続されて
いる他のシリンダ列を有する内燃機関と一緒に回転する
排ガスタービン過給機の装入空気圧縮機を介してか、又
は、燃料の供給を遮断されたシリンダ列の追加の吸引弁
を介して周囲から直接的に、行われる。この運転状態の
間においては、停止された排ガスタービン過給機の空気
圧縮機の中及び燃料の供給を遮断された内燃機関のシリ
ンダ列の装入空気導管部分の中には、何らの正の圧力も
存在しない。それ故、封鎖空気シールの機能のために必
要な周囲圧力以上の圧力は無くなる。潤滑油の供給は、
排ガスタービン過給機の一時的な停止の間も中断されな
い。それ故、封鎖空気圧の無い場合には、潤滑油は封鎖
シールを通って漏れる。漏れた潤滑油は、停止された排
ガスタービン過給機の排ガスタービン及び装入空気圧縮
機のうず形室の中にプールとして集まる。排ガスタービ
ン過給機の運転の開始の際に、漏れた潤滑油のプール
は、その装入空気圧縮機のうず形室から装入空気の流れ
により、装入空気集合管の中に引き抜かれるが、このこ
とは、付属するシリンダ列の中に運転を危険とさせる過
熱を生じさせる。また、排ガスタービンに漏れた潤滑油
は粘着し、更に、制御不能な排ガスの燃焼を生じさせ、
羽根車及び排ガス設備の運転を危険とする障害を生じさ
せる。German Patent 23 38 952 discloses a reciprocating piston internal combustion engine of the type described above, in which one exhaust gas turbine supercharger is associated with each cylinder bank of the internal combustion engine. In order to minimize the loss of lubricating oil, the rotor of the exhaust gas turbocharger is provided with a so-called closed air seal, in which compressed air is supplied from the charging air line of the reciprocating piston internal combustion engine. . When the supply of fuel to one cylinder row of the internal combustion engine is cut off, the associated exhaust gas turbine supercharger is stopped by cutting off the supply of exhaust gas to the turbine. The supply of air to a cylinder row driven as a compressor, which is cut off from the fuel supply, is charged to an exhaust gas turbine supercharger that rotates together with an internal combustion engine having another cylinder row that continues to operate. This can be done either via an air compressor or directly from the surroundings via an additional suction valve in the bank of cylinders with the fuel supply cut off. During this operating state, no positive air flow is present in the air compressor of the exhaust gas turbine supercharger which has been stopped and in the charge air conduit section of the cylinder bank of the internal combustion engine which has been cut off from the supply of fuel. There is no pressure. Therefore, there is no pressure above ambient pressure necessary for the function of the closed air seal. The supply of lubricating oil is
It is not interrupted during the temporary shutdown of the exhaust gas turbocharger. Therefore, in the absence of blocking air pressure, the lubricating oil leaks through the blocking seal. The leaked lubricating oil collects as a pool in the vortex chamber of the exhaust gas turbine of the stopped exhaust gas turbine supercharger and the charge air compressor. At the start of operation of the exhaust gas turbine supercharger, the leaked pool of lubricating oil is drawn into the charging air collecting pipe by the flow of charging air from the vortex chamber of the charging air compressor. This causes overheating in the associated cylinder row which makes operation dangerous. In addition, the lubricating oil that leaks to the exhaust gas turbine sticks and causes uncontrolled combustion of the exhaust gas.
It causes an obstacle that makes the operation of the impeller and the exhaust gas equipment dangerous.

それ故、本発明の課題は、無負荷又は減少された部分負
荷の下における運転時間内において、幾つかのシリンダ
列への燃料の供給の遮断及びそれに付属する排ガスター
ビン過給機の停止の後にも、また、装入空気集合管の中
に周囲空気圧力以上の圧力が維持されたままである往復
動ピストン内燃機関を得ることにあるのである。The object of the present invention is therefore to provide, within the operating time under no load or a reduced partial load, after shutting off the supply of fuel to several rows of cylinders and stopping the associated exhaust gas turbine supercharger. It also consists in obtaining a reciprocating piston internal combustion engine in which the pressure above the ambient air pressure is maintained in the charge air collecting pipe.

この課題は、本発明によると、「請求の範囲」第１項の
特徴項に記載される構成により達成される。本発明の他
の形態は、「請求の範囲」第２〜５項の記載から得られ
る。本発明により達成される利点は、特に、燃料の供給
を遮断されたシリンダ列に対して空気の供給を停止する
ことにより、運転中の排ガスタービン過給機の空気流れ
が、最善の運転範囲内の運転及び改善された圧力条件を
生じさせること、無負荷及び部分負荷の際に、周囲空気
圧力以上の装入空気圧力が装入空気導管系統内に達成さ
れること、燃料の供給を遮断されたシリンダ列を有する
運転時間の間に、停止された排ガスタービン過給機の装
入空気圧縮機も、また、吸入側に配置された遮断装置の
ために、装入空気導管系統の中を支配している装入空気
圧力を作用されること、増加された装入空気圧力により
両方の排ガスタービン過給機の回転子における封鎖空気
シールが十分に圧力空気を供給され、うず形室の中への
潤滑油の流出を阻止すること、燃料の供給を遮断されて
いないシリンダ列への良好な装入空気の供給により、往
復動ピストン内燃機関の無負荷及び部分負荷における運
転が改善されることなどにある。This object is achieved, according to the invention, by the features described in the characterizing part of the first section of the "claims". Other aspects of the invention can be derived from the recitations of claims 2-5. The advantages achieved by the present invention are that the air flow of the operating exhaust gas turbine supercharger is kept within the optimum operating range, in particular by shutting off the air supply to the bank of cylinders which have been de-energized Operating conditions and improved pressure conditions, at no load and at partial load, a charge air pressure above ambient air pressure is achieved in the charge air conduit system, the fuel supply is cut off. During the operating time with a row of cylinders, the charge air compressor of the exhaust gas turbine supercharger also stopped in the charge air conduit system due to the blocking device located on the suction side. The charge air pressure being applied to the exhaust gas turbine supercharger rotor is increased by the charge air pressure being increased, and the closed air seals in the rotors of both exhaust gas turbine superchargers are supplied with sufficient pressure air into the spiral chamber. Prevent the outflow of lubricating oil It, by the supply of good charging air to the cylinder row that is not shut off the supply of fuel, in such that the operation in the no-load and partial load of the reciprocating piston internal combustion engine is improved.

本発明の実施例が、図面に略図により示されており、以
下にそれに基づいて本発明を詳細に説明する。図面は 第１図は、２群のシリンダ列及び２群の並列的に作動を
する排ガスタービン過給機を有している過給される多シ
リンダ往復動ピストン内燃機関を示す略図； 第２図は、燃料の供給を遮断することが可能であるシリ
ンダ列を有する遮断可能な装入空気導管部分の種々の実
施例を示す略図； である。Embodiments of the invention are shown diagrammatically in the drawings, on which the invention will be described in detail. The drawings are: Fig. 1 is a schematic diagram showing a supercharged multi-cylinder reciprocating piston internal combustion engine having two groups of cylinder rows and two groups of exhaust gas turbine superchargers operating in parallel; FIG. 4 is a schematic diagram showing various embodiments of a shut-off charge air conduit section having a cylinder bank capable of shutting off fuel supply;

第１図に示すように、往復動ピストン内燃機関が２群の
シリンダ列11及び12から成り立っており、これらのシリ
ンダ列11,12は、装入空気導管19から、それぞれ、１個
の装入空気導管部分13,14を介して、あらかじめ圧縮さ
れた装入空気を装入される。シリンダ列11ないしは12
は、排ガス導管部分15,16を配置されており、これらの
導管部分15,16は、排ガス集合管路34に流入している。
装入空気の供給は、往復動ピストン内燃機関に配置され
た、並列的に作動をする２群の排ガスタービン過給機1
7,18により行われ、また、これらの過給機17,18は、そ
れぞれ、排ガスタービン25ないし26は装入空気圧縮機24
ないしは27から成り立っている。As shown in FIG. 1, the reciprocating piston internal combustion engine is composed of two groups of cylinder rows 11 and 12, and each of these cylinder rows 11 and 12 is fed from a charging air conduit 19 into a charging cylinder. Pre-compressed charge air is introduced via the air conduit sections 13, 14. Cylinder row 11 or 12
The exhaust gas conduit sections 15, 16 are arranged, and these conduit sections 15, 16 flow into the exhaust gas collecting line 34.
The charge air is supplied to the reciprocating piston internal combustion engine by two groups of exhaust gas turbine superchargers 1 operating in parallel.
7 and 18, and these superchargers 17 and 18 are exhaust gas turbines 25 to 26, respectively.
Or consists of 27.

排ガスタービン過給機18は、排ガス導管39の中に配置さ
れた、制御可能な閉塞装置30により開閉自在に形成され
ている。往復動ピストン内燃機関の減少された排ガスの
供給の下における運転時間の際には、排ガスタービン過
給機18を停止の下に、装入空気の供給は、もっぱら排ガ
スタービン過給機17により行われる。排ガスタービン過
給機18の停止の間に、装入空気圧縮機27を通って何らの
装入空気も逃げることが出来ないように、装入空気吸引
導管36の中には自動的に閉塞する閉塞装置37が配置され
ている。The exhaust gas turbine supercharger 18 is formed so as to be openable / closable by a controllable closing device 30 arranged in an exhaust gas conduit 39. During the operating time of the reciprocating piston internal combustion engine under reduced exhaust gas supply, the exhaust gas turbine supercharger 18 is stopped and the charge air is supplied exclusively by the exhaust gas turbine supercharger 17. Be seen. During the shutdown of the exhaust gas turbine supercharger 18, the charge air suction conduit 36 is automatically blocked so that no charge air can escape through the charge air compressor 27. A closure device 37 is arranged.

排ガスタービン25,26は入口側において、排ガス導管38,
39を介して排ガス集合導管34に、出口側において排気導
管31に、それぞれ、連結されている。On the inlet side, the exhaust gas turbines 25, 26 have exhaust gas conduits 38,
It is connected to the exhaust gas collecting conduit 34 via 39 and to the exhaust conduit 31 on the outlet side.

装入空気圧縮機24,27は、装入空気吸引導管35ないし36
は連結されており、圧縮された装入空気を導管20,21及
び装入空気冷却器22,23を介して装入空気集合導管19に
供給する。圧力油により潤滑されている排ガスタービン
過給機17,18のそれぞれには、潤滑油の漏れ止めの封鎖
空気シールが回転子に配置されており、これらのシール
は、それぞれ、導管28ないしは29を介して装入空気導管
20ないしは21から圧力空気を供給される。The charge air compressors 24 and 27 include charge air suction conduits 35 to 36.
Are connected to each other and supply the compressed charge air to the charge air collecting conduit 19 via the conduits 20 and 21 and the charge air coolers 22 and 23. Each of the exhaust gas turbine superchargers 17, 18 which is lubricated by pressure oil is provided with a sealing air seal for the leakage of the lubricating oil on the rotor, which seals respectively the conduits 28 or 29. Charge through the air conduit
It is supplied with pressurized air from 20 or 21.

詳細には示されていない燃料供給の遮断のための装置に
よって、無負荷運転及び部分負荷運転の際に、シリンダ
列12は停止され、出力の提供無しにシリンダ列11と一緒
に回転する。シリンダ列12への燃焼の供給の遮断の際に
おける弁の制御時間に変わらないので、燃料の供給を遮
断された状態のシリンダ列12の中においても装入サイク
ルが行われる。無負荷運転及び部分負荷運転において
は、往復動ピストン内燃機関の排ガスの排出は小さい。
無論、排ガスタービン過給機18の停止の際には、たと
え、燃料の供給を遮断されたシリンダ列12の装入空気の
要求は、圧縮機24により補助されなければならないにも
かかわらず、排ガスタービン過給機17による排ガスの提
供は、周期空気圧力以上の装入空気を生成するためには
余りにも小さな駆動力を提供するだけである。装入空気
圧力が余りにも低い場合、あるいは、装入空気圧力が無
い場合には、両方の排ガスタービン過給機17,18の回転
子の封鎖シールは、もはや、機能を行いことが出来ず、
従って、潤滑油は封鎖空気シールを通って通過すること
が出来るようになる。By means of a device for shutting off the fuel supply, which is not shown in detail, the cylinder train 12 is stopped during unloaded and part-load operation and rotates with the cylinder train 11 without providing power. Since the valve control time does not change when the supply of combustion to the cylinder row 12 is cut off, the charging cycle is performed even in the cylinder row 12 in which the fuel supply is cut off. In no-load operation and part-load operation, exhaust gas of the reciprocating piston internal combustion engine is small.
Of course, when the exhaust gas turbine supercharger 18 is stopped, even if the demand for the charging air of the cylinder row 12 which is cut off from the fuel supply must be assisted by the compressor 24, The provision of exhaust gas by the turbine supercharger 17 only provides a driving force that is too small to generate charged air above the cyclic air pressure. If the charge air pressure is too low, or if there is no charge air pressure, the rotor sealing seals of both exhaust gas turbine superchargers 17, 18 can no longer perform their function,
Thus, the lubricating oil will be able to pass through the enclosed air seal.

第１図に示すように、燃料の供給を遮断されたシリンダ
列12の装入空気集合導管19と、装入空気導管部分14との
間に配置された転換装置32が救済手段を構成している。As shown in FIG. 1, the conversion device 32 arranged between the charging air collecting conduit 19 of the cylinder row 12 and the charging air conduit portion 14 of which the supply of fuel is cut off constitutes a rescue means. There is.

シリンダ列12に対する燃料の供給の遮断の際には、転換
装置32の操作により装入空気集合導管19と装入空気導管
部分14との間の連結が遮断される。同時に、転換装置32
は装入空気導管部分14と、周囲に流通している吸引開口
33との間に連結を作るが、この吸引開口33は、燃料の供
給を遮断されたシリンダ列12への空気の供給に役立つ。
運転状態にある排ガスタービン過給機17は、それ故、燃
料の供給を遮断されたシリンダ列12における空気量の要
求から免除される。しかしながら、排ガスタービン25
は、シリンダ列12からのガスの流れと、燃料を供給され
るシリンダ列11からの排ガスの流れとから成り立ってい
る排ガスの流れにより作動をする。排ガスタービン過給
機17の圧縮機24は、それから生ずる増加された駆動出力
により好適な運転領域内において作動をし、これによ
り、周囲空気圧力以上の装入空気圧力を装入空気導管1
3,19,20,21の中に確立する。それ故、常に、封鎖空気シ
ールの作動に対して十分な周囲空気圧力以上の圧力があ
る。When the supply of fuel to the cylinder row 12 is cut off, the connection between the charge air collecting conduit 19 and the charge air conduit portion 14 is cut off by operating the converter 32. At the same time, the conversion device 32
Is the charging air conduit portion 14 and the suction opening circulating around it.
This suction opening 33 serves for the supply of air to the cylinder row 12 which is blocked from the supply of fuel, although a connection is made to it.
The exhaust gas turbine supercharger 17 in operation is therefore exempt from the demand for the amount of air in the cylinder row 12 with the fuel supply cut off. However, the exhaust gas turbine 25
Operates with an exhaust gas flow consisting of a gas flow from the cylinder line 12 and an exhaust gas flow from the cylinder line 11 supplied with fuel. The compressor 24 of the exhaust gas turbine supercharger 17 operates in the preferred operating range due to the increased drive power resulting therefrom, which results in a charge air pressure above ambient air pressure of the charge air conduit 1
Established in 3,19,20,21. Therefore, there will always be a pressure above ambient air pressure sufficient for the operation of the closed air seal.

各装入空気導管部分13,14の中には、安全迅速封鎖装置4
0が配置されており、この装置40は、機関の運転パラメ
ータ（例えば、潤滑油の温度又は圧力など）が、機関の
機械的な強度を危険とするような極端な値である危険な
場合には、ピストン内燃機関の迅速な停止のために封鎖
される。転換装置32は、装入空気導管部分14の中の安全
迅速封鎖装置40に装入空気の流れ方向において前方に配
置されている。Within each charge air conduit section 13, 14 is a safety and quick closure device 4
0 is arranged, and this device 40 is used when the operating parameter of the engine (for example, the temperature or pressure of the lubricating oil) is an extreme value that makes the mechanical strength of the engine dangerous. Are blocked for a quick stop of the piston internal combustion engine. The diverter 32 is arranged forward of the safety and quick closure device 40 in the charge air conduit section 14 in the direction of charge air flow.

第２図においては、転換装置32が、制御可能な装置43
と、これと無関係な構成要素として吸入開口33とから形
成されている。この場合、吸入開口33は、逆止め弁44を
付属されており、この逆止め弁44は、制御可能な装置43
の貫通位置において支配している装入空気圧力により閉
鎖されたままとされ、また、シリンダ列12の燃料の供給
の遮断の下における運転の場合には開放される。In FIG. 2, the conversion device 32 comprises a controllable device 43.
And a suction opening 33 as a component unrelated to this. In this case, the intake opening 33 is associated with a check valve 44, which is a controllable device 43.
In the penetrating position, it remains closed due to the prevailing charging air pressure and, in the case of operation under interruption of the supply of fuel to the cylinder row 12, it opens.

第３図においては、転換装置32及び安全迅速封鎖遮断装
置40が、組み合わせ装置として形成されている。迅速遮
断位置においては、吸入開口33の装入空気導管部分14へ
の貫通は、阻止体41により封鎖される。In FIG. 3, the conversion device 32 and the safety and quick blocking device 40 are formed as a combined device. In the quick shut-off position, the penetration of the intake opening 33 into the charge air conduit section 14 is blocked by the blocking body 41.

第４図に示す変形においては、装入空気導管部分14の封
鎖のための装置及び安全迅速封鎖装置が、一つの転換装
置42に組み合わされている。この実施例においては、吸
引開口33から装入空気導管部分14への貫通が、制御可能
な装置45により封鎖可能に形成することが必要である。
吸引開口33は、迅速遮断装置が作動された時又はシリン
ダ列12が燃料を供給された時に封鎖される。In the variant shown in FIG. 4, the device for the closure of the charge air conduit section 14 and the safety quick closure device are combined in one conversion device 42. In this embodiment, it is necessary that the penetration from the suction opening 33 into the charge air conduit section 14 be made blockable by a controllable device 45.
The suction opening 33 is closed when the quick shut-off device is activated or when the cylinder row 12 is supplied with fuel.

Claims (5)

【特許請求の範囲】[Claims] 【請求項１】並列に作動をする多数の排ガスタービン過
給機を有している過給多シリンダ往復動ピストン内燃機
関であって、排ガスタービン過給機の内の少なくとも１
個が、選択的に運転及び停止が可能であるように形成さ
れており、また、往復動ピストン内燃機関が、無負荷運
転又は部分負荷運転の間にシリンダ列の幾つかへの燃料
の供給を遮断するための手段を有しており、燃料供給の
遮断により他のシリンダ列と一緒に動かされるシリンダ
列が、残りのシリンダ列の装入空気の供給とは無関係に
空気を供給されるようになっている過給多シリンダ往復
動ピストン内燃機関において、幾つかのシリンダ列への
燃料の供給が遮断された時でさえも排ガスタービン過給
機の中に周囲空気圧以上の圧力を維持するために、並列
に作動をするすべての排ガスタービン過給機（17,18）
に対して共通の装入空気集合導管（19）が配置されてい
ることと、運転及び停止が可能である排ガスタービン過
給機（18）がその装入空気圧縮機（27）の吸引側に逆止
め弁（37）を含んでいることと、燃料の供給が遮断可能
であるシリンダ列（12）に付属する装入空気導管部分
（14）が、制御可能な装置（32）により装入空気集合導
管（19）から封鎖可能に形成されていることと、前記排
ガスタービン過給機（18）を排ガス集合導管（34）から
隔離することにより同排ガスタービン過給機（18）の運
転を選択的に停止させる制御可能な閉塞装置（30）が設
けられていることと、燃料の供給の遮断可能なシリンダ
（12）への装入空気の供給のために付属される装入空気
導管部分（14）に吸引開口（33）が配置されることを特
徴とする過給多シリンダ往復動ピストン内燃機関。1. A supercharged multi-cylinder reciprocating piston internal combustion engine having a plurality of exhaust gas turbine superchargers operating in parallel, at least one of the exhaust gas turbine superchargers.
Are configured to be selectively operable and deactivatable, and a reciprocating piston internal combustion engine supplies fuel to some of the cylinder banks during no-load or part-load operation. Cylinder rows having means for shutting off, which are moved together with other cylinder rows by shutting off the fuel supply, are supplied with air independently of the supply of charging air for the remaining cylinder rows. In a supercharged multi-cylinder reciprocating piston internal combustion engine, in order to maintain a pressure above ambient air pressure in the exhaust gas turbine supercharger even when the fuel supply to some cylinder rows is cut off. , All exhaust gas turbine superchargers working in parallel (17,18)
Is equipped with a common charge air collecting conduit (19) and an exhaust gas turbine supercharger (18) that can be operated and stopped is on the suction side of the charge air compressor (27). Including the check valve (37) and the charge air conduit part (14) attached to the cylinder row (12) which can interrupt the supply of fuel, the charge air is controlled by the controllable device (32). Operation of the exhaust gas turbine supercharger (18) is selected by forming the exhaust gas turbine supercharger (18) so as to be able to be blocked from the exhaust gas turbine supercharger (18). A controllable closure device (30) for stopping the fuel supply, and a charge air conduit portion (for supplying charge air to a cylinder (12) capable of interrupting the supply of fuel). Supercharging multi-cylinder reciprocating motion characterized in that suction opening (33) is arranged in 14) Ston internal combustion engine. 【請求項２】制御可能な装置（32）及び吸引開口（33）
が、転換装置（32）として一緒に形成されている請求の
範囲第１項記載の過給多シリンダ往復動ピストン内燃機
関。2. Controllable device (32) and suction opening (33).
2. A supercharged multi-cylinder reciprocating piston internal combustion engine according to claim 1, characterized in that they are formed together as a converter (32). 【請求項３】転換装置（32）が、装入空気導管部分（1
4）の中に配置されている安全迅速遮断装置（40）と一
緒にされている請求の範囲第２項記載の過給多シリンダ
往復動ピストン内燃機関。3. A conversion device (32) comprising a charge air conduit section (1).
4. A supercharged multi-cylinder reciprocating piston internal combustion engine according to claim 2, together with a safety and quick disconnect device (40) located in (4). 【請求項４】装入空気導管部分（14）の封鎖のための装
置及び安全迅速遮断装置（42）が、一つの転換装置（4
2）に組み合わされており、また、吸引開口（33）から
装入空気導管部分（14）への貫通が制御可能な装置（4
5）により封鎖可能に形成されている請求の範囲第２項
記載の過給多シリンダ往復動ピストン内燃機関。4. A device for blocking the charging air conduit section (14) and a safety quick shut-off device (42) are one conversion device (4).
2) and with controllable penetration from the suction opening (33) to the charge air conduit section (14) (4)
The supercharged multi-cylinder reciprocating piston internal combustion engine according to claim 2, which is formed so as to be able to be closed by (5). 【請求項５】吸引開口（33）が制御可能に形成されてい
る請求の範囲第４項記載の過給多シリンダ往復動ピスト
ン内燃機関。5. The supercharged multi-cylinder reciprocating piston internal combustion engine according to claim 4, wherein the suction opening (33) is controllably formed.
JP62505593A 1987-02-17 1987-09-23 Supercharged multi-cylinder reciprocating piston internal combustion engine with multiple exhaust gas turbine superchargers operating in parallel Expired - Lifetime JPH0758051B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE3704967A DE3704967C1 (en) 1987-02-17 1987-02-17 Supercharged multi-cylinder reciprocating internal combustion engine with several exhaust gas turbochargers working in parallel
DE3704967.4 1987-02-17
PCT/DE1987/000432 WO1988006232A1 (en) 1987-02-17 1987-09-23 Supercharged multicylinder reciprocating combustion engine with several exhaust gas turbochargers operating in parallel

Publications (2)

Publication Number Publication Date
JPH02500042A JPH02500042A (en) 1990-01-11
JPH0758051B2 true JPH0758051B2 (en) 1995-06-21

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ID=6321159

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JP62505593A Expired - Lifetime JPH0758051B2 (en) 1987-02-17 1987-09-23 Supercharged multi-cylinder reciprocating piston internal combustion engine with multiple exhaust gas turbine superchargers operating in parallel

Country Status (9)

Country Link
US (1) US4903489A (en)
EP (1) EP0302082B1 (en)
JP (1) JPH0758051B2 (en)
KR (1) KR920001747B1 (en)
CN (1) CN1006484B (en)
DE (2) DE3704967C1 (en)
ES (1) ES2005384A6 (en)
SU (1) SU1709920A3 (en)
WO (1) WO1988006232A1 (en)

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Also Published As

Publication number Publication date
DE3764957D1 (en) 1990-10-18
WO1988006232A1 (en) 1988-08-25
ES2005384A6 (en) 1989-03-01
US4903489A (en) 1990-02-27
KR920001747B1 (en) 1992-02-24
EP0302082B1 (en) 1990-09-12
JPH02500042A (en) 1990-01-11
EP0302082A1 (en) 1989-02-08
DE3704967C1 (en) 1988-05-11
SU1709920A3 (en) 1992-01-30
CN1006484B (en) 1990-01-17
CN87107024A (en) 1988-08-31
KR890700740A (en) 1989-04-27

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